Refrigerant expander compressor

ABSTRACT

An expander compressor unit for a vapor compression refrigeration system is disclosed. The unit has a rotor which is provided with radial passageways terminating in tangentially oriented nozzles for expanding the high-pressure fluid and utilizing the kinetic energy of the expanding fluid to propel the rotor. The rotor is in driving engagement with a compressor which serves to compress fluid in the cycle. By this means the expander compressor unit substantially improves the efficiency of the cycle through efficient expansion of the refrigerant prior to evaporization and through reduction of the net work input into the system.

United States Patent [191 Goldsberry [451 Feb. 4, 1975 REFRIGERANTEXPANDER COMPRESSOR [75] Inventor: Fred L. Goldsberry, Amarillo, Tex.

[73] Assignee: Lone Star Gas Company, Dallas,

Tex.

[22] Filed: Dec. 7, 1973 [21] Appl. N0.: 422,759

[52] U.S. C1. 417/406, 415/80 [51] Int. Cl. F0411 17/00 [58] Field ofSearch 417/406; 415/80 [56] References Cited UNITED STATES PATENTS1,454,286 5/1923 Johnson 415/80 Primary Examiner-C. J. Husar Attorney,Agent, or FirmRichards, Harris & Medlock [57] ABSTRACT An expandercompressor unit for a vapor compression refrigeration system isdisclosed. The unit has a rotor which is provided with radialpassageways terminating in tangentially oriented nozzles for expandingthe high-pressure fluid and utilizing the kinetic energy of theexpanding fluid to propel the rotor. The rotor is in driving engagementwith a compressor which serves to compress fluid in the cycle. By thismeans the expander compressor unit substantially improves the efficiencyof the cycle through efficient expansion of the refrigerant prior toevaporization and through reduc tion of the net work input into thesystem.

12 Claims, 6 Drawing Figures PATENTEUFEB H975 sum 10F 3 /CONDENSERCOMPRESSOR fi m EXPANDER COMPRESSOR /EVAPORATOR PATENTEDFEB 41%3,864.06?

* SHEET 20F 3 60 IO 44 14 4a PATENTEUFEB 41975 3.864.065

SHEET 30F 3 1 REFRIGERANT EXPANDER COMPRESSOR BACKGROUND AND SUMMARY OFTHE INVENTION The present invention relates generally to refrigerationsystems, and more particularly, to an expander compressor unit whichutilizes the work expended in direct expandion of a refrigerant to powera turbine which drives a small compressor to aid the primary compressorof a refrigeration system in compressing gaseous vapors from evaporatorpressure to condenser pressure.

Vapor compression refrigeration cycles and apparatus for carrying outthese cycles are well known. In theoretical vapor compressionrefigeration, saturated vapor refrigerants at low pressure enter acompressor and undergo isentropic compression. The high pressure vaporenters a condenser and heat is rejected from the fluid at constantpressure from the condenser. The working fluid leaves the condenser as asaturated liq- .uid. An isenthalpic throttling process follows across anexpansion valve or capillary tube. The working fluid is then evaporatedat constant pressure with the working fluid absorbing heat to completethe cycle.

In the past, the design of'direct expansion refrigeration units has notgenerally taken advantage of the energy or available work lost in theexecution of the cycle through the throttling or free expansion of theliquid refrigerant into the evaporator of the refrigeration machine.Generally, only limited use has been made of the conversion intomechanical energy of the kinetic energy possessed by the refrigerantwhich flows from the high pressure side to the low pressure side of therefrigeration system. For example, it is known to power a compressorwith the refrigerant discharged from the capillary tube. The compressoris arranged in the auxiliary circuit which includes a second evaporator.In this way, a two temperature system is provided in which theadditional evaporator can be operated within a temperature range lowerthan that of the evaporator in the main circuit. Typical of systems ofthis type is the refrigeration system method shown in US. Pat. No.2,519,010. r I

Other attempts at utilizing the kinetic energy of refrigerant expansionhave concentrated mainly on pumping or recirculating refrigerant orlubricants. For example, US. Pat. No. 2,763,995 discloses the use ofhigh pressure refrigerant directed against the blades of a turbine. Theturbine has a shaft which is connected to a centrifugal pump. The pumpserves to recirculate oil rich liquid refrigerant back to thecompressor.

Generally, however, systems as described above which utilize or attemptto utilize the work expanded in the throttling or expansion process havenot found wide acceptance. As pointed out, most of these systems attemptto utilize the kinetic energy to perform some auxiliary operation suchas the circulation of lubricating fluid. Accordingly, the equipmentnecessary for its recovery has not been thought to be economicallyfeasible. Very little work has been done in utilizing this energy toimprove the performance and efficiency of the basic vapor compressionrefrigeration cycle.

The present invention provides an expander compressor in which thesaturated liquid from the condenser is'expanded and flashed throughnozzles of a shaft mounted rotor causing a tangential propelling forceto be applied to the rotor and an attached turbine shaft. The turbineshaft drives an axial compressor unit. On the compressor side, saturatedvapor from the evaporator enters the vane chamber of the compressor andis compressed into the super heat region and is discharged into anannular chamber either to the primary compressor or directly to thecondenser of the air conditioning unit. A small fraction of thesaturated liquid refrigerant entering the unit is utilized to providefull film lubrication of the shaft bearings. The compressor section ofthe unit may include an appropriate inducer section to pull therefrigerant into the blades of the compressor section. The rotor can bemodified for various capacity systems by changing the nozzle size or byadding more discharge passages to the expander section.

DESCRIPTION OF THE DRAWINGS The above and other objects and advantagesof the present invention will become apparent from reading the followingclaims, specifications and drawings in which:

FIG. 1 is a graphical representation of a vapor compressionrefrigeration cycle onthe temperature (T) and ent opy (S) coordinates;

FIG. 2 is a schematic representation of the vapor compressionrefrigeration cycle;

FIG. 3 is a longitudinal sectional view showing the expander compressorof the present invention;

FIG. 4 is a sectional view taken along lines 44 of FIG. 3;

FIG. 5 is a longitudinal sectional view showing another embodiment ofthe expander compressor of the present invention; and

FIG. 6 is a sectional view taken along lines 66 of FIG. 5.

DETAILED DESCRIPTION The theoretical ideal cycle for vapor compressionrefrigeration is shown in FIG. 1 and represented as cycle l,2,3,4,l. Thecycle of operation is shown in the T-S plane. Point 1 represents thestate of the refrigerant entering the compressor. Usually in this statethe refrigerant is nearly dry saturated vapor. The saturated vapor atlow pressure enters the compressor and undergoes adiabatic compression1-2. During the compression, the refrigerant is usually super-heated. Instate 2, the super-heated vapor passes into the condenser and is cooledat constant pressure and then condensed at constant temperature. Heat isrejected in the process 2 to 3. The working fluid leaves the condenseras a saturated liquid. A throttling process follows from 3-4 and theworking fluid is then evaporated in process 4 to I, to complete thecycle. During the evaporation process, the refrigerant is vaporized. Asis well known in thermodynamics, the amount of heat (QL) removed by therefrigerant is represented by the change in entropy occurring in theprocess 4 to l as projected on the horizontal coordinate as a-b. Thework (W) expended in achieving this amount of heat removal representedalong ab is represented by the energy expended in compression from 1 to2 as seen in FIG. I. The coefficient of performance (COP) of arefrigeration cycle is represented by the equation:

COP QL/W The present invention utilizes conversion of the kinetic energyof the refrigerant to mechanical energy to drive a turbine in the systemlocated between the condenser and the evaporator. The high pressurerefrigerant is expanded through nozzles located on a turbine rotor. Theturbine is mechanically connected to drive a centrifugal compressorlocated downstream of the evaporator which serves to partially compressthe refrigerant prior to entry at the intake of the main compressor. Theschematic representation of the system of y the present invention isshown in FIG. 2.

As the vapor mixture reaches the evaporator at lowerentropy, the vapor.is able to absorb an additional amount of heat equal to the workdissipated by the fluid in reaching the evaporator to the expanderturbine. Referring to FIG. 1, isentropic expansion through the nozzle isshown by the dotted line 3-4. Thus the amount of heat which can beabsorbed by the refrigerant in the evaporator is increased by the amountrepresented between a'-a on the entropy coordinate.

The second mechanism by which the overall efficiency or coefficient ofperformance of the refrigeration cycle is improved is through thereduction of the amount of external work brought in the system duringcompression of the refrigerant between 1 and 2. Thus by compressing orpartially compressing the gas exiting from the evaporator, the suctionpressure on the compressor is increased and the amount of work broughtexternally into the system is reduced.

FIGS. 3 and 4 show in detail the expander compressor of the presentinvention. The machine of the present invention is generally designatedby the numeral 10. The unit has cooperating housing members 12 and 14which respectively define the expander section 13 and compressor section15 of the machine. Housing sections 12 and 14 may be integrally joinedor may be cooperatively fitted together at annular threaded section 16.Housing section 12 is formed with a projecting boss 18. Boss 18 is boredat 20 for reception of precision shaft bearing 21 which are pressed intothe bore. Circular expansion chamber wall 33 is generally concentricwith bore 20. The radial face 26 of housing portion 12 is provided witha concentric series of labyrinth seals 28 formed in the surface. Outletport 30 communicates with expansion chamber 24 near the periphery of thechamber.

Compressor chamber 34 is formed in housing member 14 by peripheralsurface 31 and generally convex surface 32. Boss 36 axially projectsfrom housing member 14 and is counterbored at 38 for reception ofprecision shaft bearings 39. Axial inlet passageways 40 and 41communicate with compressor chamber 34 through boss 36.

The turbine unit'is generally designated by the nun 1eral44 and includesan expander rotor 46 and a compressor section 48. Turbine unit 44 ismounted on axial shaft 50 which has its opposite ends mounted onrotation in bearings 21 and 39 in the expansion and compression sectionsof the unit. Tubine 44 is preferably of steel or a high qualityprecision molded or machined synthetic such as nylon. An axialpassageway 51 extends through shaft 50 communicating at the expanderside with inlet 25 in boss 18. Inlet 25 is internally threaded toaccommodate a refrigerant line fitting. Small radial clearancepassageways 52 and 53 are provided in the bearing bores at the oppositeend of shaft 50 to permit fluid within axial passageway 51 to beadmitted to bearings 21 and 39 for lubrication.

Rotor 46 of turbine 44 has a generally circular peripheral edge 55which, with housing wall 33, defines the annular expansion chamber 24. Aplurality of radial passages 56 extend in rotor 46 and communicate withaxial passageway 51. As best seen in FIG. 4, the ends of radiallyopposite passageways 56 terminate in oppositely directed tangentialnozzles 58. The number and location of the passageways 56 and associatednozzles 58 will vary with the capacity of the refrigeration unit. It isto be understood that evenly spaced, oppositely disposed passageways andnozzles are required so that expanding fluid exerts a balancedtangential force to propel the turbine rotor. Expansion chamber 24 issealed by labyrinth seals 28 and 29 provided on the parallel radialsurfaces of housing section 12.

The compressor side of turbine 44 includes a generally circular impellerplate 60 which has one surface in sealing engagement with labyrinthseals 28. A plurality of compressor vanes 62 are radially positioned onthe opposite side of impeller plate 60. As seen in FIG. 3, the vanes areformed having outer converging edge 64 which closely cooperates withinterior housing surface 32. The outer tip of the compressor vanes 62and housing wall 31 define annular compressor chamber 34. Outlet 65communicates with chamber 34 and is adapted to be connected in therefrigeration system.

With the expander compressor unit connected in a refrigeration system asshown schematically in FIG. 2, the operation of the unit will be asfollows. A saturated liquid refrigerant is supplied to the expandercompressor unit 10 at inlet 25. The liquid refrigerant flows into axialpassageway 51 and is admitted along radial passageways 52 and 53 tolubricate bearings 21 and 39 at the opposite ends of shaft 50. The highpressure saturated liquid refrigerant also flows through radialpassageways 56 in the rotor and expands and flashes through nozzleopenings 58 at the ends of passageways 56. The expansion through nozzles58 imparts a tangential force propelling turbine 44. The rotor andnozzle arrangement is a particularly efficient expansion device. Theexpansion through the nozzle is substantially isentropic. The energynormally lost by expansion through a valve or capillary is conserved inthe instant case with the resulting two phase mixture having lesservelocity than a mixture having been expanded through an expansion valve.The discharge from the nozzle enters the annular exhaust chamber 24 at alower quality than if the mixture had been expanded through a fixednozzle. The mixture is discharged from chamber 24 at passage 30 where itenters the evaporator.

On the compressor side 15 of the unit, saturated vapor returning fromthe evaporator enters the compressor at passages 40 and 41. The rotatingvanes 62 compress the entering vapor into the superheat region and thevapor is admitted into annular compressor chamber 34 and is dischargedat passageway 65. From discharge passageway 65 the pressurized vaporflows either to the primary compressor or directly to the condenser ofthe apparatus.

Another embodiment of the present invention is shown in FIGS. 5 and 6and is generally designated by the numeral 70. The unit of embodiment 70includes a housing 71 enclosing expander section 72 at one end and acompressor section 73 at the other end. The interior of housing 71 has agenerally cylindrical-bore 74 enclosed by end plate 84. A series ofannular labyrinth seals 76 are peripherally arranged in bore 74. Anannular expander chamber 75 is provided in the housing wall.

In the compressor end of the unit, the interior of chamber bore 74 has aradially outwardly converging end wall 77 which defines compressorchamber 94.

A turbine member 80 is rotatively mounted within housing 71 at oppositestub shafts 81 and 82 supported in appropriate non-friction bearings 83.The turbine rotor 85 has cylindrical outer surface 86 in closerelationship with bore 74. An axial passage 88 in stub shaft 81communicates with radially extending passages 89. Bleed passageways 78and 79 provide for positive lubrication of bearings 83 with liquidrefrigerant. The end of radial passages 89 communicate with chamber 75across nozzles 90 propelling turbine 80 with a tangential force. Nozzles90 preferably are in threaded engagement at the end of passage 89 tofacilitate replacement with various other size nozzles to change thecapacity of the unit.

Forwardly curved inducer blades 92 are located in compressor section 73immediately adjacent the inlet 93 to the compressor section.lnducer'blades 92 serve a to induce or pull the saturated vapor into thecompressor section. Compression takes place by means of the rotatingreversed-curved compressor blades 95 which impart energy to the fluid asit flows along the impeller blades. Discharge from compression chamber94 is at outlet 96.

In operation, the expander compressor of the present embodiment issimilar to that described above with reference to the previousembodiment. Saturated liquid is supplied at inlet passage 81 to theunit. The saturated liquid expands and flashes through nozzles 90causing a tangential force propelling the turbine 80. The

effecient operation there is also need for torque matching between theexpander and the compressor.

The present compressor expander provides a unit which can substantiallyincrease the efficiency of a vapor compression refrigeration cycle. Asexplained, a small expander boosts performance in cooling machines bytwo mechanisms: l) removal of energy from the saturated liquid vapormixture as it enters the evaporator to improve the heat absorbentcapability of the mixture; (2) reduction of the amount of work requiredexternally to the system. Thus, with the present invention the equationfor coefficient of performances becomes Note that with the presentinvention that should the turbine fail to function, there is noappreciable loss to the system. However, any work transferred throughthe turbine centrifugal compressor adds considerably to the performanceof the cycle.

An example of the increased efficiency theoretically obtainable with thepresent invention has been worked out for a simple refrigeration cycleworking between 140 F and F, assuming reasonable efficiencies for allmechanical components:

FROM THE PROPERTIES TABLE FOR F-l2 s,,., .08024 SM q m -03680 q M 1 3)11,, 41.24 38.70 2.5(BTU/lbm) isentropic work input to cycle l1(BTU/lbm) adiabatic expansion heat removal 41.5(BTU/lbm) COP 4l.5/1l/.93.681 (.9) 3.3954

COP Heat Removed Isentropic Work*Expansion Eff Work Re d. IsentropicWork Exp. Eff. Comp. Eff. Comp. E%f.

flashed vapor liquid is discharged into annular chamber and from thereit enters the evaporator. A small fraction of the saturated liquidrefrigerant may be diverted to the bearing annulus area through bleedpassageways 78 and 79 to provide for full film lubrication of the rotorbearings. On the compressor side, saturated vapor from the evaporatorenters inlet 93 assisted by the inducer blades 92. The saturated vaporis compressed into the superheat region by compressor vanes 95 anddischarged into the compressor chamber and finally through dischargepassageway 96 to either the compressor or directly to the condenser inthe air conditioning unit. The high and low pressure side of the unitare separated by peripheral labyrinth seals 76.

It will be noted that in embodiment 70 of FIG. 5, the rotor section ofthe turbine is of greater diameter than the turbine compressor blades.Several considerations must be taken into account to insure that theexpander can operate efflciently as an isentropic expander. For

COP, (41.5 2.5 .70)/([11/9] 2.5 .70* .70) 43.25/10.997 3.932

COP 3.3954

super churned Increase 15.72%

Thus from the foregoing, it will be seen that the present inventionprovides an expander compressor adaptable for use with conventionalvapor compression refrigeration cycles. The unit is simple having anintegral single piece expander and centrifugal compressor rotor withoutan intermediate bearing support. The expander turbine uses the flashedand saturated liquid propulsion energy that is generally not utilized inconventional systems. The use of the liquid refrigerant for simple fullpressure general bearing lubrication adds to the efficiency of the unit.

It will be obvious to those skilled in the art to make changes andmodifications to the device of the present invention. To the extent thatthese changes, alterations and modifications do not depart from thespirit and bearing means supporting the shaft for rotation relative tothe housing;

means sealing said first chamber from said second chamber;

a rotor fixedly mounted on said shaft for rotation therewith in saidfirst chamber, said rotor including a fluid passageway communicatingbetween the inlet passageway of the shaft and nozzle means adapted toeffect fluid discharge generally tangentially into said first chamber toimpart rotation to said rotor by reaction to the fluid discharge fromthe nozzle means; and

impeller means mounted on said shaft in said second chamber and driventhereby, said impeller means adapted to compress fluids introducedthereto.

2. The rotary device of claim 1 wherein said shaft is mounted inantifriction bearings and wherein lubrication passage means communicatesaid bearings with said fluid inlet passageway to provide positivelubrication to the bearings by means of the same fluid that isdischarged from the nozzle means.

3. The rotary device of claim 1 wherein said rotor diameter exceeds thediameter of said impeller.

4. An expander compressor comprising:

a housing defining an expander chamber having an inlet and an outlet anda compressor chamber having an inlet and an outlet;

axially aligned bores oppositely arranged in said housing;

bearings mounted in said opposite bores;

an axially extending shaft mounted in said bearings for rotationrelative to the housing, said shaft defining an axial fluid receivingpassageway having an inlet at one end defining said expander chamberinlet;

lubricating passage means connecting said axial fluid receivingpassageway with said bearings to effect lubrication of the bearings bymeans of the received fluid;

a rotor fixedly mounted on said shaft in said expander chamber;

at least one pair of oppositely arranged discharge passageways in saidrotor, each of said discharge passageways communicating with said axialpassageway in the shaft and terminating in a nozzle for dischargingfluid into said annular chamber in a generally tangential direction andthereby rotating the rotor and the shaft by reaction to the discharge offluid from the nozzles;

means sealing said first and second chambers; and

rotary compressor means mounted on said shaft in said compressorchamber, said compressor means including a generally circular plate onsaid shaft, vane means radially projecting from said shaft on said platewhereby the energy of expansion drives said rotary compressor.

5. The expander compression of claim 4 wherein said sealing meanscomprise labyrinth seals in the housing walls.

6. An expander compressor comprising:

a housing defining a generally circular bore:

axially aligned bores oppositely arranged in said housing;

bearings mounted in said opposite bores;

an axially extending shaft mounted in said bearings for rotationrelative to the housing, said shaft defining an axial fluid receivingpassageway having an opening at one end;

a cylindrical rotor fixedly mounted on said shaft for rotationtherewith, the periphery of said rotor defining with said bore anexpansion chamber and having an end face defining a compressor chamberwith said bore;

inlet and discharge passageways communicating with said expansion andcompressor chamber;

at least a pair of oppositely arranged radial discharge passageways insaid rotor communicating with said fluid receiving passageways in theshaft, each of said passageways terminating in a nozzle for dischargingfluid into said expansion chamber generally tangentially with respect tosaid discharge pas sageways and thereby rotating the rotor and the shaftby reaction to the discharge of fluid from the nozzles;

sealing means at the rotor periphery sealing said ex pansion chamber;and

a plurality of compressor vanes carried on said end face of said rotorin said compressor section adapted to compress fluids.

7. The expander compressor of claim 6 further including inducer bladescarried on said shaft adjacent said compressor chamber inlet to assistin inducing flow from said compressor inlet through said compressorvanes.

8. The expander compressor of claim 7 wherein said compressor vanes arerearwardly curved with respect to the direction of rotation of saidrotor.

9. The expander compressor of claim 8 wherein said inducer blades areforwardly curved with respect to the direction of rotation of saidrotor.

10. The expander compressor of claim 6 wherein said sealing meanscomprises a series of labyrinth seals in the housing wall engaging saidrotor periphery.

11. The expander compressor of claim 6 wherein lubricating passagewaysare provided in said rotor and shaft for directing fluid from the fluidreceiving passageway to the bearings and thereby lubricating thebearings.

12. An expander compressor comprising:

a housing member;

a rotor member rotatively secured in said housing,

said rotor having an axial inlet passageway communicating with at leasttwo opposite radial discharge passageways terminating in nozzles adaptedto discharge tangentially with respect to said radial passagewayswhereby pressurized fluid admitted at said inlet expands through saidnozzles into said housing to rotate said rotor by reaction to the fluiddischarge from the nozzles; and

vane means operatively connected to said rotor for rotation therewithand adapted to compress fluids delivered thereto.

1. A rotary device comprising: a housing having first and secondchambers, each chamber having a discharge passageway; an axiallyextending shaft mounted in said housing and extending into the first andsecond chambers, said shaft having a fluid inlet passageway formedtherein; bearing means supporting the shaft for rotation relative to thehousing; means sealing said first chamber from said second chamber; arotor fixedly mounted on said shaft for rotation therewith in said firstchamber, said rotor including a fluid passageway communicating betweenthe inlet passageway of the shaft and nozzle means adapted to effectfluid discharge generally tangentially into said first chamber to impartrotation to said rotor by reaction to the fluid discharge from thenozzle means; and impeller means mounted on said shaft in said secondchamber and driven thereby, said impeller means adapted to compressfluids introduced thereto.
 2. The rotary device of claim 1 wherein saidshaft is mounted in antifriction bearings and wherein lubricationpassage means communicate said bearings with said fluid inlet passagewayto provide positive lubrication to the bearings by means of the samefluid that is discharged from the nozzle means.
 3. The rotary device ofclaim 1 wherein said rotor diameter exceeds the diameter of saidimpeller.
 4. An expander compressor comprising: a housing defining anexpander chamber having an inlet and an outlet and a compressor chamberhaving an inlet and an outlet; axially aligned bores oppositely arrangedin said housing; bearings mounted in said opposite bores; an axiallyextending shaft mounted in said bearings for rotation relative to thehousing, said shaft defining an axial fluid receiving passageway havingan inlet at one end defining said expander chamber inlet; lubricatingpassage means connecting said axial fluid receiving passageway with saidbearings to effect lubrication of the bearings by means of the receivedfluid; a rotor fixedly mounted on said shaft in said expander chamber;at least one pair of oppositely arranged discharge passageways in saidrotor, each of said discharge passageways communicating with said axialpassageway in the shaft and terminating in a nozzle for dischargingfluid into said annular chamber in a generally tangential direction andthereby rotating the rotor and the shaft by reaction to the discharge offluid from the nozzles; means sealing said first and second chambers;and rotary compressor means mounted on said shaft in said compressorchamber, said compressor means including a generally circular plate onsaid shaft, vane means radially projecting frOm said shaft on said platewhereby the energy of expansion drives said rotary compressor.
 5. Theexpander compression of claim 4 wherein said sealing means compriselabyrinth seals in the housing walls.
 6. An expander compressorcomprising: a housing defining a generally circular bore; axiallyaligned bores oppositely arranged in said housing; bearings mounted insaid opposite bores; an axially extending shaft mounted in said bearingsfor rotation relative to the housing, said shaft defining an axial fluidreceiving passageway having an opening at one end; a cylindrical rotorfixedly mounted on said shaft for rotation therewith, the periphery ofsaid rotor defining with said bore an expansion chamber and having anend face defining a compressor chamber with said bore; inlet anddischarge passageways communicating with said expansion and compressorchamber; at least a pair of oppositely arranged radial dischargepassageways in said rotor communicating with said fluid receivingpassageways in the shaft, each of said passageways terminating in anozzle for discharging fluid into said expansion chamber generallytangentially with respect to said discharge passageways and therebyrotating the rotor and the shaft by reaction to the discharge of fluidfrom the nozzles; sealing means at the rotor periphery sealing saidexpansion chamber; and a plurality of compressor vanes carried on saidend face of said rotor in said compressor section adapted to compressfluids.
 7. The expander compressor of claim 6 further including inducerblades carried on said shaft adjacent said compressor chamber inlet toassist in inducing flow from said compressor inlet through saidcompressor vanes.
 8. The expander compressor of claim 7 wherein saidcompressor vanes are rearwardly curved with respect to the direction ofrotation of said rotor.
 9. The expander compressor of claim 8 whereinsaid inducer blades are forwardly curved with respect to the directionof rotation of said rotor.
 10. The expander compressor of claim 6wherein said sealing means comprises a series of labyrinth seals in thehousing wall engaging said rotor periphery.
 11. The expander compressorof claim 6 wherein lubricating passageways are provided in said rotorand shaft for directing fluid from the fluid receiving passageway to thebearings and thereby lubricating the bearings.
 12. An expandercompressor comprising: a housing member; a rotor member rotativelysecured in said housing, said rotor having an axial inlet passagewaycommunicating with at least two opposite radial discharge passagewaysterminating in nozzles adapted to discharge tangentially with respect tosaid radial passageways whereby pressurized fluid admitted at said inletexpands through said nozzles into said housing to rotate said rotor byreaction to the fluid discharge from the nozzles; and vane meansoperatively connected to said rotor for rotation therewith and adaptedto compress fluids delivered thereto.